Transmission



R. CHILTON TRANSMISSION May 19, 1936.

Filed Deo. 27, 1934 4 Sheets-Sheet 1 www 1N VENT OR. Xabi/VD CHILTONATTORNEY.

R. CHILTON May 19, 1936.

TRANSMIS S ION NHT INVENTOR. OZHMD CHfz TON R. CHILTON May 19, 1936.

TRANSMISSION 4 Sheets-Sheet 4 Filed Dec. 27, 1954 INVENTOR. OLHN (WILTNPatented May 19, 1936 UNITED STATES PATENT OFFICE TRANSMISSION RolandChilton, Ridgewood, N. J.

Application vDecember 27, 1934, Serial No. 759,349

30 Claims. (Cl. 74 281) My invention relates to variable speedtransmissions, and is concerned more particularly with variable speedtransmissions wherein driving members are loaded into non-slippingcontact.

. The invention comprises a new organization wherein rolling membershave driving contacts subtending relatively variable pitch cone angles,and may be said to constitute a continuing development of that type ofvariable speed transmission described and illustrated in previouslyilled applicationa'to wit: Serial No. 669,144, iiled May 3, 1933; SerialNo. 728,056, led May 29, 1934; Serial No. 742,751, filed September 7,1934; Serial No. 742,752, filed September 7, 1934; Seria-l No. 743,515,filed September 11, 1934; and Serial No. 746,958, led October 5, 1934'.

The specic features of the present invention which should be emphasizedare:

(a) The transmission is of double-sided form;

(b) It is of the rigid disc, tilting roller variety;

(c) The variable pitch cone angle contact member is the driven member; l

(d) The small pitch cone angle member comprises a bevel gear, and is thefixed or reaction (e) The large pitch cone angle member comprises abevel gear, and is the driving member;

(f) The transmission is of the double roller type:

(g) The large and small angle bevel gears are applied to different setsof rollers;

(h) The roller bevel pinions are disposed at the inner ends of therollers;

(i) The two sets of rollers are separated and drivably connected byintermediate annular driving rings;

(j) The rings comprise parts of the control mechanism;

(k) The control is hydraulic.

(l) Torque-responsive action is eiected by a pump having a torque-loadedrelief valve;

(m) The pump pressures are eiectlve on the outer connecting rings, i.e., those urging the transmission to low gear (high ratio) whereforeloading of the relief valve is from the torque on the xed or reactionmember;

(n) A second pump is effective onthe inner connecting ring, and thepressure in this system is proportioned from that in the rst system by apiston in the latter and a relief valve in the former, connected by afloating pump having a movable fulcrum, comprising the control lever ofthe transmission.

Alternatives to items (a) to (i) inclusive, have been disclosed in myvarious copending applications above identified. The novel features andadvantages of the present invention resides more particularly in thestructures concerned with items-(7') to (n), inclusive.

Other features of the invention will be pointed out hereinafter.

In the drawings, wherein like reference characters denote like orcorresponding parts:

Fig. 1 is a longitudinal section on the line Ii-II of Fig.2;

Fig. 2 is an axial view in which the left hand part is in outside view;the right hand part is in section on the line |2a|2a of Fig. 1, whilethe lower segment is a fragmentary section on the line |2b of Fig. 1,with a portion shown in outside view;

Fig. 3 reproduces a portion of the section of Fig. 1 on an enlargedscale;

Fig. 4 is an isometric View of the rockable roller spindle mechanism;and

Fig. 5 is a detail view showing the driving connection between the cagespindle caps.

In its broadest aspect the present invention is generally similar to theseveral embodiments described and illustrated in said previously filedapplications in that it includes radial rollers supported in a cage andengaged by large, small, and variable pitch cone angle members,respectively. It comprises a driving means, a driven means, a xed orreaction means, and a rotationally oating means. Specifically, the smallangle member is normally xed to constitute the reaction member; thelarge angle member constitutes the driving member; the variable contactangle member constitutes the driven member; while the rollers shown arefree to planetize with respect to these various members. Such adisposition gives a Variable speed ratio range extending from 1 to 0, to1 to 1, and, if desired, therebeyond into reverse or over-speed ratios,or, as one alternative, the variable angle contact member may be xed, inwhich case the ratio range extends from 1 to 1 in both directions toinfinity, giving a range of zero to infinitely fast rotation of thedriven member (the latter being impossible of practical realization,although Within the actual, theoretical kinematic properties of theorganization).

Referring rst to Fig. 1, represents the crankshaft end of a conventionalengine, equipped with a back plate |0|, to which a main housing |02 ofthe transmission is secured by studs |03. The crankshaft |00 carries theusual flywheel |04 secured by bolts |05, which also secure a splineddriving member |06. In this member there is splined a hub |01 of aroller clutch cam |08, cooperating with rollers |09, and a cylindricalportion |0, to form a conventional one-way clutch. A main or drivingshaft is provided with a bushing ||2 whereby the shaft is piloted Withinthe clutch cam |01, |08, and this main shaft is further provided withsplines 3, .carrying a hub H4 of the member ||0 which has an externalilange to which is secured a bevel gear H6.

l This end of the shaft is supported in a bearinner ends of the rollers|51.

ing ||8 clamped in a sleeve ||9 of a cover plate |20 secured to thefront wall |2| of the housing |02 by bolts |22 (Fig. 2).

At its rear end the main shaft has an extension |23 on which is piloteda driven sleeve |24 having a llange |26 bolted to a rear driven member|21 as shown. The sleeve |24 has splined upon it a coupling member |28secured by a nut |29 which also serves to clamp a bearing |30 wherebythe driven member assemblage is located axially relative to the housing.

The driving shaft is further provided with a flange |3 I, to theexterior of which there is drivably engaged by dogs |32, a (preferablynon-metallic) driving gear |33 located between a cage |34 and a thrustnut |35 thereon, and engaging the bevel pinion |64.

The reaction member of the transmission comprises a bevel gear |36,located between a second cage |31 and a thrust nut |38 thereon andprovided with dogs |39, slidably engaging companion dogs in a sleeve |40having a torque arm |4|, which is restrained from rotation by a ball |42cooperating with sloping pockets |43 formed in the arm |4|, and in anopposing button |44 set in the front wall |2|.

A front end driven disc |45 is tied to the rear driven disc |21 by anencircling drum |46. This drum is provided with inturned projections |41cooperating with mating projections |46 on the driven discs |45|21comprising a bayonet type joint secured by screws |49. The forward endof the driven member assemblage is supported on a bushing |50 free torotate on the sleeve |40 of the reaction member torque arm.

Meshed with the reaction gear |36 are a plurality of bevel pinions |5|integral with journals |52 supported in long bushings |53 in the cage|31, andeach pinion is provided with a spherical head |54 provided withshort splines |56, engaged, for slight angular freedom, with splines vinthe The rollers are supported for rotation on spindles |58 on bushings|60, the spindles being integral with rectangular heads |6 which are ofarcuate profile about the center of the splines |56 of the bevel pinions|5|.

The exterior' of the cage |31 is proled to similar radius, and a cap |62of similar arcuate prole has an arcuate recess accommodating theintegral head I6 I, when the cap is secured on the cage by the capscrews |63.

By this construction, which is also illustrated4 in the isometric viewof Fig. 4, each roller and spindle assembly is free for slight tippingaction in its own radial plane, but is rigidly held to radial alignmentwith the corresponding pinion shaft as will be clear from Fig. 4 and thelower segment of Fig. 2.

The construction of the rollers of the rear cage |34 is similar to thatalready described for the front cage assembly. The two cages areconnected together for unitary rotation (within and independently of,the drum |46) by interlocking extensions |65 on the caps 62, whereby thecages are free for slight axial movement. (Fig. 5.)

Engaged between the outer ends of the two sets of rollers is an annularpiston member |66 cooperating with an annular cylinder member |61, eachhaving similar crowned annular contact faces |66 engaging the outer endsof the respective sets of rollers. The member |66 is splined at |69 forrotation with the member |61, these members comprising a compositedriving ring between the outer ends of the rollers.

Rotationally free within this outer ring is a similar composite drivingring between the inner ends of the rollers, comprised by the members|10-|1| which have engaging end splines |12. and are free for rotationon the driving shaft on sleeves |13 and |14 on which the cages |31- |34are also rotationally free.

The outer intermediate ring |66 is provided with segmental centrifugalweights |15 having a tapered engagement between that member and theannular nutl |16. Both intermediate members are provided with U-sectionhydraulic packing rings. as shown, to prevent oil leakage, and the innermember |10 is further provided with an exterior groove |`11 with whichthe oil passages |18|19 communicate, the groove being sealed by suitablerings |60.

Formed on the one-way clutch member |0 are helical gear teeth |6|engaging the helical pinion |92 (Fig. 2) which drives the oil pumps|63-|64. The delivery of the latter communicates both with the externalconnection |65, and to a large diameter valve seat |86 formed in thepump body. with which seat there cooperates the fiat face of the torquearm |4|, so that, due to the action -of the ball |42 in the inclinedpockets |43|44 any tendency of the torque arm ,fto rotate, in eitherdirection, will move it to the left of Fig. 1 against the hydraulicpressure existing over the area of the valve seat |66. This flat-endedtorque arm accordingly forms a relief valve for the pump |64 whereby thepressure delivered by this pump is always proportional to the torque onthe reaction gear |36, which is yanchored exclusively through the torquearm |4|. This torque responsively regulated pressure is led, through theexternal pipe |81 by the `connection |66 to the under side of thepressure-responsive plunger |69, and this pressure is at all timeseffective on the piston area of the outer connecting rings |66-|61 byway of the passages |90, |9|, |92, |93, |94 and nally through thepassages |18, |19 already described.

Similarly, the other pressure pump |63 delivers to the connection |95(Fig. 2) and by'an external pipe (not shown) to the passage |96 beneaththe relief valve plunger |91, and from thence to the piston area of theinnerV intermediate rings |10, |1|, through the passages |96, |99, 200,20| and 202. Y

The pressure-responsive plunger |89, and the relief valve plunger |91are connected by the floating rocking beam 203 with which is engaged theV--shaped end of the control lever 204 which comprises a movable fulcrumfor this pressure proportioning beam. ,Y

It will now be seen that there are two individual hydraulic systems, oneeffective on the piston area of the outer intermediate rings, and theother on the piston area of the inner intermediate rings. The pressurein the outer system is at all times proportional to the torque on thereaction gear |36, the torque arm of which comprises the relief valve ofthe pump by which this outer" system pressure is generated. The pressurein the inner system is proportioned to the pressure in the outer systemsince the restraining load on the inner system relief valve |91 isderived from the pressure on the plunger |69 of the outer system, thisproportion being determined by the position of the control lever 204along the lloating rocking beam 203. It should be noticed that theplunger |89 in no way modifies the pressure in the outer system which isdetermined exclusively by the reaction gear torque, this plunger |88serving merely as the datum from which the pressure in the outer systemis proportioned by the control lever.

The slope of the ball pockets |43, |44; the radius of these pockets inthe torque arm Ill; the' area of the valve seat |86 and the piston areaof the outer intermediate members are so proportioned that the contactpressure on these outer rings is always suiilciently in excess of theinstantaneous driving load thereon as to prevent slippage. It should nowbe obvious that, if, for example, the piston area of the inner"intermediate ring were made equal to that of the outer rings, then therocking action of the rollers would transfer their contact pointsagainst the driven discs, from end to end, in direct proportion to themovement of the control lever from end to end of the rocking beam. Thisproportion will not be direct with unequal piston areas, which wouldmerely modify the position of the control lever for any specific ratioposition, without departing from the important characteristic that thepressure on the driven member is the sum of the pressures on theintermediate members. If the contact of these last members is on thepitch cone angles of the driving and reaction bevel gears respectively,then the torque transmitted by each will equal the torque on therespective gears, and we have already seen that the torque on the drivenmember is the sum of these torques, whereby the contact load at eachdriving contact is proportional to the instantaneous force beingtransmitted thereat in all ratio positions, and despite variations inthe power transmitted.

From the large circumference of the relief valve seat |86 of the outersystem, it will be clear that the height of the opening required torelieve the pressure to a low figure will be very small, and that hencethe parts may be adjusted for a very small backlash at the torque arm.

A refinement, as a precautionary measure to locate the mean position ofthe inner intermediate rings |10, I1I, and to limit them to equal andopposite motion, to ensure that there will be v no errors in the equaland opposite tilting of the two sets of rollers, as might occur frombodily longitudinal acceleration of the whole transmission, Vwill now bedescribed. It comprises a locating member 2 I0 which is equipped withherring bone teeth 2II of equal and opposite helix angle engaging rightand left hand internal teeth or splines 2I2, 2I3 formed in the membersIII, I1I; and is located axially on the main shaft III on the sleeve 2I4between the ring 2I5 and the flange I3I. 'Ihis main shaft in turn islocated axially relative to the transmission as a whole by the longbushing 2 I 6 screw-threaded as shown into the driven sleeve I24 whichhas already been described as axially located in the transmission by thebearing |38. The nut 2 I 1 completes this location of the shaft I I Iwhile the screwthreads onthe bushing 2I6 permit of a iine adjustmentwhereby the rollers may be brought to equal angularity at initialassembly. It should be clear that, as the members |10, I1| are splinedtogether at |12 against relative rotation and have right and left handconnections of equal helix angle with the axially located member 2I0,these intermediate members are restrained to equal and oppositemovement, and are positvely prevented from unitary displacement whichwould upset the accurate angular relation of the rollers.

Ffrom the foregoing, as well as from the mode of operation as set forthin said companion applications, the operation of the instantorganization should be obvious. By rocking the rollers to shift thepoint of contact longitudinally of the roller length, the driving ratiois progressively shifted from 1 to 1, to 1 to 0, or vice versa. Shift ofthe roller contact is obtained hydraulically through manipulation of thecontrol lever 288.

description is unnecessary. It should be mentioned, however, that theinclusion of the oneway drive clutch ,between the engine and the drivingshaft has to do with this regenerative system.

While I have described my invention in detail in its present preferredembodiment, it will be obvious to those skilled in the art, afterunderstanding my invention, that various changes and modifications maybe made therein without departing from the spirit or scope thereof. Iaim in the appended claims to cover all such modifications and changes.

What is claimed is:

1. In a transmission, in combination, opposed annular discs, rollersrockably engaging said discs.' rings in rolling driving contact withsaid rollers, and means associated with said rings adapted to effectsaid rocking.

2. In a transmission, in combination, opposed annular discs, rollersrockably engaging said discs, intermediate rings drivably connectingsaid rollers, and hydraulic means associated with said rings adapted toeffect said rocking.

3. In a transmission, in combination, opposed annular discs rigidlyspaced, rollers 'engaging the respective discs, and axially separablerings drivably connecting said rollers.

4. A transmission including, in combination, planetary bevel pinions,rollers rockable with respect to said pinions, means to rock saidrollers and a driving coupling between said rollers and pinons organizedto permit of said rocking.

5. In a transmission, axially separable driving rings, and meansincluding an axially located member having splined engagement withrespective rings of equal but opposite helical angles to restrain saidrings to equal and opposite movement. y

6. In a transmission, in combination, rockable rollers, and roller driverings including pistons adapted to effect said rocking by fluid pressureacting on said pistons.

7. In a transmission, in combination, opposed annular discs, rollersrockably engaging said discs, rings intermediately located between andin rolling driving contact with said rollers, and'means to effect saidrocking by relatively moving said rings.

8. In a transmission, the combination with axially separable drivemembers restrained from pressure pump, a pressure relief valvecomprising a reactive abutment for said member, a second pump, a reliefvalve for said second pump, means to load the last said valve inproportion to the pressure developed by the first said pump, and controlmeans to vary said proportion at will.

10. In a transmission having members to be loaded into non-slippingdriving contact, a loading means comprising a piston, a pressure pumpserving said piston, and a pressure control valve for -said pump subjectto load derived from the torque on one of said drive members.

11. A torque-responsive contact load means for transmission drivemembers including in combination, a pump, a pressure'relief valvetherefor, and means to apply to said valve a force proportional to thedriving reaction on one of said members.

12. In a transmission, in combination, a drive member, a pressure pump,a drive member loading piston subject to pump pressure, a pressurerelief valve, and means to load said valve in proportion to the drivingeiort on said member.

13. The combination with transmission `members including a rocker to beloaded and shifted, of pistons eiective at respective ends of said 4rocker, pumps adapted to hydraulically load the respective pistons,means adapted to vary the pressure from one of said pumps in proportionto the torque on one of said drive members, and control means adapted toproportion the relative pump pressures.

f. 14. In a transmission, in combination, drivably contacted members,two contact load pistons, uid pumps serving the respective pistons,

' automatic means to vary the pressure of one said pump'in proportion tothetorque on the associated member, and control means to vary at willthe relative pressure of the other pump.

- 15. In a transmission, a reaction member, 'a pressure pump, and apressure relief valve comprising a reactive abutment -for said memberwhereby the pressure generated by said pump is.V

automatically proportioned to the instantaneous reaction load on said"member.

16. In a transmission, a reaction member, a pressure pump, a pressurerelief valve comprising a reactive abutment for said member, a secondpump, a relief valve therefor, and means to load the last said valve inproportion to the pressure developed by the iirst said pump.

17. In a transmission, the combination with al rotary member comprisinga fluid operated piston, of means to balance the eiectvof centrifugalforce on the uid comprising centrifugal weights organized to impress anopposing force upon the piston.

18. In a. transmission, in combination, opposed annular discs, a rollerrockably engaging one said disc, a roller rockably engaging the othersaid disc, rings intermediately located between and drivably connectingsaid rollers, and means to axially separate said rings to eiect saidrocking.

19. In a transmission, in combination, opposed annular discs, a rollerrockably engaging one said disc, a roller rockably engaging the othersaid disc, said rollers being rockable toward and from one another attheir respective ends, rings intermediately located between and drivablyconnect- 'ing said rollers, and means to axially separate said rings toeiect said rocking.

20. In a transmission, in combination, opposed annular discs, rollersrockably engaging said discs, a'pair of rings intermediately locatedbetween and in rolling driving contact with said rollers, said ringsbeing axially movable to effect said rocking, and means to control therelative movement of said rings.

21. In a transmission, in combination, opposed annular discs, rollersengaging the respective discs, and means intermediately located betweenand in rolling driving contact with said rollers.

22. In a transmission, in combination, axially separable driving rings,and means including a member having splined engagement with said ringsto restrain said rings to equal and opposite movement.

23. In a transmission, in combination, opposed annular discs, a rollerrockably engaging one said disc, a roller rockably engaging the othersaid disc, a pair oi outer rings intermediately located between anddrivably connecting said rollers adjacent to their outer ends, a pair ofinner rings intermediately located between and drivably connecting saidrollers adjacent to their inner ends, andmeans to axially separate oneor the other of said pairs of rings to effect said rocking.

24. In a transmission, in combination, opposed i annular discs, a rollerrockably engaging one said disc, a roller rockably engaging the othersaid disc, a pair of interconnected rings intermediately located betweenand drivably connecting said rollers adjacent to one end thereof, a pairof interconnected rings intermediately located be-v tween and drivablyconnecting said rollers adjacent to the opposite end thereof, and meansto axially move one said pair of rings toward one another as the othersaid pair of rings is axially separated and vice versa, the relativemovement of said pairs of rings being adapted to effect said rockingwithout disturbixig the driving connection between said rollers whichsaid pairs of rings afford.

25. In a transmission, in combination, planetary bevel pinions, rollersrockable with respect to said pinions, and a splined connection betweeneach said roller and its associated pinion organized for unitaryrotation of said rollers and pinions in all rocked positions of saidrollers.

26. In a transmission, in combination, a planetary carrier, a bevelpinion organized to planetize with said carrier, a roller rockable withrespect to said pinion, a driving connection between said pinion and,roller organized to permit of ysaid rocking, and means for guiding therocking movement of said roller movable with said carrier.

27. A rockable support for a transmission roller comprising, incombination, an annular cage member having arcuate slots, and a rollerspindle having an arcuate integral head portion engaged within saidslots and movable crosswise y said member.

28. In a transmission, a planet carrier having an arcuate profile, a capsecured to the prole of said carrier and deiining therewith opposedarcuate guide slots, a planetary spindle radially disposed with respectto said guide slots and hav*- ing a head portion engaged4 therein, and aroller coaxial with and rotatable on the spindle axis.

29.111` a transmission, in combination, a roller spindle having asubstantially rectangular head, arcuate in lateral aspect, a rollercoaxial with and rotatable on the spindle axis, and a carrier memberhaving guides engaging said arcuate head.

30. In a transmission, in combination, a rotary member including afluid-operated piston, and means movableboth with and with respect tosaid piston to impress thereon a force eiective to balance thecentrifugal force on the fluid resulting from said rotation.

ROLAND CHlLTON.

